WO2018164022A1

WO2018164022A1 - Hydraulic oil control valve and valve timing regulation device

Info

Publication number: WO2018164022A1
Application number: PCT/JP2018/008200
Authority: WO
Inventors: 哲朗満谷
Original assignee: 株式会社デンソー
Priority date: 2017-03-07
Filing date: 2018-03-05
Publication date: 2018-09-13
Also published as: DE112018001233B4; US20190368387A1; CN110291275A; JP6790925B2; US11248502B2; JP2018145906A; CN110291275B; DE112018001233T5

Abstract

An outer sleeve (40) is formed cylindrically. An inner sleeve (50) is formed cylindrically and is provided inside the outer sleeve (40). A supply flow passage (501) is formed extending radially through the inner sleeve (50) and allows hydraulic oil from a hydraulic oil supply source (8) to flow therethrough. An axial flow passage (502) is formed extending axially between the outer sleeve (40) and the inner sleeve (50), has one end to which the supply flow passage (501) is open, and has the other end capable of being connected to a valve timing regulation device (10). A supply check valve (71) is provided in the axial flow passage (502) on the outer side of the supply flow passage (501) in the radial direction of the inner sleeve (50), is capable of permitting hydraulic oil to flow from the supply flow passage (501) side to the axial flow passage (502) side, and is capable of preventing hydraulic oil from flowing from the axial flow passage (502) side to the supply flow passage (501) side.

Description

Hydraulic oil control valve and valve timing adjustment device

Cross-reference of related applications

This application is based on Patent Application No. 2017-42607 filed on March 7, 2017, the contents of which are incorporated herein by reference.

The present disclosure relates to a hydraulic oil control valve and a valve timing adjusting device using the hydraulic oil control valve.

Conventionally, hydraulic oil control valves that control the flow of hydraulic oil are known. For example, in Patent Document 1, an inner sleeve is provided inside a cylindrical outer sleeve, and a check valve that is elastically deformable in a radial direction is provided in an annular space formed between the outer sleeve and the inner sleeve. Yes. The check valve controls the flow of hydraulic oil between the outside and the inside of the outer sleeve and the inner sleeve.

US Pat. No. 6,899,126

In the hydraulic oil control valve of Patent Document 1, when hydraulic oil flows from the outside of the outer sleeve to the inside of the inner sleeve via the check valve, it is necessary to bypass the outer edge portion of the check valve, so that the flow path pressure loss is large. There is a risk.
Further, in the hydraulic oil control valve of Patent Document 1, when a large amount of hydraulic oil flows from the outside of the outer sleeve to the inside of the inner sleeve via the check valve, the check valve closes the flow path of the inner sleeve, There is a risk that the flow of hydraulic oil to
Further, when the hydraulic oil flows from the inside of the inner sleeve to the outside of the outer sleeve via the check valve, the same problem as described above may occur.
An object of the present disclosure is to provide a hydraulic oil control valve and a valve timing adjustment device that have a small flow path pressure loss and can suppress unintended flow path blockage.

The present disclosure is a hydraulic oil control valve capable of controlling a flow of hydraulic oil supplied from a hydraulic oil supply source to a hydraulic oil supply target, and includes an outer sleeve, an inner sleeve, a supply flow path section, an axial flow path section, and a supply And a check valve.

The outer sleeve is formed in a cylindrical shape.
The inner sleeve is formed in a cylindrical shape and is provided inside the outer sleeve.
The supply flow path portion is formed so as to penetrate the inner sleeve or the outer sleeve in the radial direction, and the hydraulic oil from the hydraulic oil supply source flows.
The axial direction flow path portion is formed so as to extend in the axial direction between the outer sleeve and the inner sleeve, the supply flow path portion opens on one end side, and the other end side can be connected to a hydraulic oil supply target.
The supply check valve is provided in the axial direction flow path section on the radially outer side of the inner sleeve or the radial direction inner side of the outer sleeve with respect to the supply flow path section, and hydraulic oil from the supply flow path side to the axial flow path side. The flow of hydraulic oil from the axial flow path portion side to the supply flow path portion side can be restricted.

In the present disclosure, the hydraulic oil that has flowed from the supply flow path section to the axial flow path section flows to the other end side of the axial flow path section without bypassing the supply check valve, and is supplied to the hydraulic oil supply target. . Therefore, the flow path pressure loss in the hydraulic oil control valve can be suppressed.
In the present disclosure, even if a large amount of hydraulic oil flows from the supply flow path portion to the axial flow path portion, the supply check valve only abuts against the wall surface facing the opening of the supply flow path portion. The directional flow path is not blocked. For this reason, unintended flow passage interruption in the hydraulic oil control valve can be suppressed.

The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings. The drawing
FIG. 1 is a cross-sectional view showing a hydraulic oil control valve and a valve timing adjusting device according to a first embodiment. 2 is a cross-sectional view taken along line II-II in FIG. FIG. 3 is a cross-sectional view showing the hydraulic oil control valve according to the first embodiment. FIG. 4 is a development view showing a supply check valve of the hydraulic oil control valve according to the first embodiment. FIG. 5 is a view showing a supply check valve of the hydraulic oil control valve according to the first embodiment, FIG. 6 is a perspective view showing an inner sleeve and a supply check valve of the hydraulic oil control valve according to the first embodiment. FIG. 7 is a cross-sectional view showing the vicinity of the supply check valve of the hydraulic oil control valve according to the first embodiment, FIG. 8 is a development view showing a recycle check valve of the hydraulic oil control valve according to the first embodiment. FIG. 9 is a cross-sectional view showing a hydraulic oil control valve according to the second embodiment, FIG. 10 is a plan view showing an inner sleeve of the hydraulic oil control valve according to the second embodiment, FIG. 11 is a cross-sectional view showing the vicinity of the supply check valve of the hydraulic oil control valve according to the second embodiment, FIG. 12 is a cross-sectional view showing the vicinity of the supply check valve of the hydraulic oil control valve according to the third embodiment, FIG. 13 is a cross-sectional view showing a hydraulic oil control valve according to the fourth embodiment, FIG. 14 is a development view showing a supply check valve of the hydraulic oil control valve according to the fifth embodiment, FIG. 15 is a cross-sectional view showing a supply check valve of the hydraulic oil control valve according to the fifth embodiment. FIG. 16 is a development view showing a supply check valve of the hydraulic oil control valve according to the sixth embodiment, FIG. 17 is a view showing a supply check valve of the hydraulic oil control valve according to the sixth embodiment. FIG. 18 is a cross-sectional view showing the vicinity of the supply check valve of the hydraulic oil control valve according to the seventh embodiment, 19 is a cross-sectional view taken along line XIX-XIX in FIG.

Hereinafter, valve timing adjustment devices according to a plurality of embodiments of the present disclosure will be described with reference to the drawings. Note that, in a plurality of embodiments, substantially the same components are denoted by the same reference numerals, and description thereof is omitted.

(First embodiment)
1 to 3 show a hydraulic oil control valve and a valve timing adjusting device according to a first embodiment. The valve timing adjusting device 10 changes the rotational phase of the camshaft 3 with respect to the crankshaft 2 of the engine 1 as an internal combustion engine to thereby change the intake valve 4 of the intake valve 4 or the exhaust valve 5 that the camshaft 3 is driven to open and close. The valve timing is adjusted. The valve timing adjusting device 10 is provided in a power transmission path from the crankshaft 2 to the camshaft 3. The crankshaft 2 corresponds to a “drive shaft”. The cam shaft 3 corresponds to a “driven shaft”. The intake valve 4 and the exhaust valve 5 correspond to “valves”.

The configuration of the valve timing adjusting device 10 will be described with reference to FIGS.
The valve timing adjusting device 10 includes a housing 20, a vane rotor 30, and a hydraulic oil control valve 11.

The housing 20 includes a sprocket 21 and a case 22. The sprocket 21 is fitted to the end of the cam shaft 3. The camshaft 3 supports the sprocket 21 in a rotatable manner. The chain 6 is wound around the sprocket 21 and the crankshaft 2. The sprocket 21 rotates in conjunction with the crankshaft 2. The case 22 has a bottomed cylindrical shape, and an open end is fixed to the sprocket 21 by a bolt 12 while being combined with the sprocket 21. The case 22 has a plurality of partition walls 23 protruding radially inward. An opening 24 that opens to a space outside the case 22 is formed at the center of the bottom of the case 22. The opening 24 is located on the side opposite to the camshaft 3 with respect to the vane rotor 30.

The vane rotor 30 has a boss 31 and a plurality of vanes 32. The boss 31 has a cylindrical shape and is fixed to the end of the cam shaft 3. The vane 32 protrudes between the partition walls 23 toward the radially outer side from the boss 31. A space 200 inside the housing 20 is partitioned into a retard chamber 201 and an advance chamber 202 by a vane 32. The retard chamber 201 is located on one side in the circumferential direction with respect to the vane 32. The advance chamber 202 is located on the other side in the circumferential direction with respect to the vane 32. The retard chamber 201 and the advance chamber 202 correspond to a “hydraulic chamber”. The vane rotor 30 rotates relative to the housing 20 in the retard direction or the advance direction according to the hydraulic pressure in the retard chamber 201 and the advance chamber 202.

The hydraulic oil control valve 11 includes an outer sleeve 40, an inner sleeve 50, a spool 60, a supply flow path portion 501, an axial flow path portion 502, a circumferential flow path portion 503, a radial flow path portion 504, a supply check valve 71,

Movement restriction parts

56, 57 and the like are provided.

In the present embodiment, the hydraulic oil control valve 11 is provided at the center of the vane rotor 30 (see FIGS. 1 and 2).
The outer sleeve 40 is formed in a substantially cylindrical shape with a material having relatively high hardness including, for example, iron. The outer sleeve 40 has an inner peripheral wall formed in a substantially cylindrical surface shape.
A threaded portion 41 is formed on the outer peripheral wall of one end portion of the outer sleeve 40. On the other end side of the outer sleeve 40, a locking portion 49 is formed that extends annularly from the outer peripheral wall outward in the radial direction.

A shaft hole 100 and a supply hole 101 are formed at the end of the cam shaft 3 on the valve timing adjusting device 10 side. The shaft hole portion 100 is formed so as to extend in the axial direction of the cam shaft 3 from the center of the end surface of the cam shaft 3 on the valve timing adjusting device 10 side. The supply hole 101 is formed to extend radially inward from the outer wall of the cam shaft 3 and communicate with the shaft hole 100.

On the inner wall of the shaft hole portion 100 of the cam shaft 3, a shaft side screw portion 110 that can be screwed to the screw portion 41 of the outer sleeve 40 is formed.
The outer sleeve 40 passes through the inside of the boss 31 of the vane rotor 30 and is fixed to the cam shaft 3 so that the screw portion 41 is coupled to the shaft side screw portion 110 of the cam shaft 3. At this time, the locking portion 49 locks the end surface of the boss 31 of the vane rotor 30 opposite to the cam shaft 3. Thereby, the vane rotor 30 is fixed to the camshaft 3 so as to be sandwiched between the camshaft 3 and the locking portion 49. As described above, the outer sleeve 40 is provided in the central portion of the vane rotor 30.

The oil pump 8 is connected to the supply hole 101. The oil pump 8 pumps up the hydraulic oil stored in the oil pan 7 and supplies it to the supply hole 101. As a result, the hydraulic oil flows into the shaft hole 100. Here, the oil pump 8 corresponds to a “operating oil supply source”. Further, the valve timing adjusting device 10 corresponds to “operating oil supply target”.

The inner sleeve 50 is formed in a substantially cylindrical shape by a material having a relatively low hardness including, for example, aluminum. That is, the inner sleeve 50 is formed of a material having a lower hardness than the outer sleeve 40. The inner sleeve 50 has an outer peripheral wall formed in a substantially cylindrical surface shape.

The inner sleeve 50 is provided inside the outer sleeve 40 so that the outer peripheral wall is fitted to the inner peripheral wall of the outer sleeve 40. The inner sleeve 50 is not movable relative to the outer sleeve 40.

On one end side of the inner sleeve 50, a sleeve plate portion 51 extending in a plate shape from the inner peripheral wall inward in the radial direction is formed. Here, the sleeve plate portion 51 is located on the radially inner side of the screw portion 41 of the outer sleeve 40, and divides the space inside the inner sleeve 50 into one side and the other side.

The spool 60 is formed in a substantially cylindrical shape from metal, for example.
The spool 60 is provided inside the inner sleeve 50 so that the outer peripheral wall slides with the inner peripheral wall of the inner sleeve 50 and can reciprocate in the axial direction.

A spool plate portion 61 extending in a plate shape from the inner peripheral wall to the inside in the radial direction is formed on one end side of the spool 60. Here, the spool plate portion 61 divides the space inside the spool 60 into one side and the other side.

A sealing portion 62 is provided at the other end of the spool 60. The sealing portion 62 has an outer peripheral wall fitted into the inner peripheral wall of the spool 60 and closes the other end of the spool 60. A substantially cylindrical internal space 600 is formed between the sealing portion 62 and the spool plate portion 61 inside the spool 60.

A variable volume space 500 is formed between the sleeve plate portion 51 and the spool plate portion 61 inside the inner sleeve 50. The volume of the variable volume space 500 changes when the spool 60 moves in the axial direction with respect to the inner sleeve 50.

In the variable volume space 500, a spring 63 is provided. The spring 63 is a so-called coil spring, and has one end in contact with the sleeve plate portion 51 and the other end in contact with the spool plate portion 61. The spring 63 biases the spool 60 to the side opposite to the sleeve plate portion 51.

A locking portion 59 is provided on the radially inner side of the other end portion of the outer sleeve 40. The locking portion 59 is formed in a bottomed cylindrical shape, and is provided so that the outer peripheral wall is fitted to the inner peripheral wall of the outer sleeve 40. A hole is formed in the center of the bottom of the locking part 59, and the sealing part 62 is located inside the hole.

The locking portion 59 can lock the other end of the spool 60 by the bottom. The locking portion 59 can regulate the movement of the spool 60 to the side opposite to the sleeve plate portion 51 of the spool 60. As a result, the spool 60 is prevented from falling off from the inner side of the inner sleeve 50.

The supply flow path portion 501 is formed on one end side of the inner sleeve 50. The supply flow path portion 501 is formed on the opposite side of the spool 60 with respect to the sleeve plate portion 51. The supply channel portion 501 is formed so as to penetrate the inner sleeve 50 in the radial direction. For example, four supply flow path portions 501 are formed at equal intervals in the circumferential direction of the inner sleeve 50.

The hydraulic fluid that has flowed in from the oil pump 8 through the supply hole 101, the shaft hole 100, and the inner sleeve 50 flows into the supply flow path 501.
Here, a filter 58 is provided on the radially inner side of the supply flow path portion 501 inside the inner sleeve 50. The filter 58 is a mesh formed in a substantially cylindrical shape. The filter 58 can collect foreign substances contained in the hydraulic oil flowing from the inner sleeve 50 to the supply flow path portion 501.

The axial flow path portion 502 is formed to extend in the axial direction between the outer sleeve 40 and the inner sleeve 50.
The axial flow path portion 502 is formed on the fitting boundary surface T 1 between the outer sleeve 40 and the inner sleeve 50 so as to be recessed radially inward from the outer peripheral wall of the inner sleeve 50.
One of the four supply flow path portions 501 connects one end side of the axial flow path portion 502 and the space inside the inner sleeve 50. That is, the supply flow path portion 501 is open on one end side of the axial flow path portion 502.

The circumferential flow path portion 503 is formed in an annular shape between the outer sleeve 40 and the inner sleeve 50, extending in the circumferential direction from one end of the axial flow path portion 502 (see FIGS. 3 and 6). That is, four supply flow path portions 501 are opened in the circumferential flow path portion 503.
The hydraulic oil that has flowed into the shaft hole 100 via the supply hole 101 can flow into the axial flow path 502 and the circumferential flow path 503 via the supply flow path 501. The hydraulic oil that has flowed into the circumferential flow path portion 503 via the supply flow path portion 501 can flow through the circumferential flow path portion 503 to the axial flow path portion 502.

The radial flow path portion 504 is formed so as to penetrate the inner sleeve 50 in the radial direction, and has one end connected to the other end side of the axial flow path portion 502 and the other end side connected to a space inside the inner sleeve 50. (See FIG. 3).

The supply check valve 71 is formed in a substantially cylindrical shape by, for example, bending a rectangular metal thin plate so that the longitudinal direction is along the circumferential direction. FIG. 4 is a developed view of the supply check valve 71. FIG. 5 is a view of the supply check valve 71 viewed from the axial direction.

The supply check valve 71 has an overlapping part 700 and a valve part 701.
The overlapping portion 700 is formed at one end of the supply check valve 71 in the circumferential direction. The overlapping portion 700 is formed so as to overlap the radially outer side of the other end portion in the circumferential direction of the supply check valve 71 (see FIG. 5). Four valve portions 701 are formed at equal intervals in the circumferential direction of the supply check valve 71.

The supply check valve 71 is provided in the circumferential flow path portion 503. The supply check valve 71 is provided so as to be elastically deformable in the radial direction at one end of the axial flow path portion 502 and the circumferential flow path portion 503. Here, the supply check valve 71 is provided so that the four valve parts 701 correspond to the four supply flow path parts 501 respectively. That is, the supply check valve 71 is provided on the radially outer side of the inner sleeve 50 with respect to the supply flow path portion 501.

The axial flow path portion 502 has a valve seat surface 52, a valve seat step surface 53, a stopper surface 42, and a stopper step surface 43.
The valve seat surface 52 is formed in an annular shape around the opening of the supply flow path portion 501 in the inner sleeve 50, and can contact the valve portion 701 of the supply check valve 71. The valve seat level difference surface 53 is formed on the radially outer side of the inner sleeve 50 with respect to the valve seat surface 52 on the other end side of the axial flow path portion 502 with respect to the valve seat surface 52 (see FIG. 7).

The stopper surface 42 is formed in the outer sleeve 40 at a position facing the opening of the supply flow path portion 501. The stopper step surface 43 is formed on the radially outer side of the outer sleeve 40 with respect to the stopper surface 42 on the other end side of the axial flow path portion 502 with respect to the stopper surface 42 (see FIG. 7).

The supply check valve 71 is provided in the circumferential flow path portion 503, and in a state where hydraulic oil does not flow through the supply flow path portion 501, that is, in a state where no external force is applied, the overlapping portion 700 is in the other circumferential direction. It is in a state where it overlaps the end (see FIG. 6). Further, the outer peripheral wall of the supply check valve 71 is located on substantially the same plane as the valve seat step surface 53 (see FIG. 7).
Here, the boundary B1 between the stopper surface 42 and the stopper step surface 43 is located within the range of the axial length of the supply check valve 71 (see FIG. 7).

When the hydraulic oil flows to the axial flow path section 502 and the circumferential flow path section 503 via the supply flow path section 501, the supply check valve 71 is pushed radially outward by the inner wall of the valve section 701 being pushed by the hydraulic oil. It is deformed so as to expand, that is, the inner diameter increases. As a result, the valve portion 701 of the supply check valve 71 is separated from the valve seat surface 52, and the hydraulic oil passes between the valve portion 701 and the valve seat surface 52, and the other end portion of the axial flow passage portion 502. It can flow to the side, that is, the radial flow path portion 504 side. At this time, the overlapping portion 700 is in a state where a part of the overlapping portion 700 is maintained while the length of the overlapping range between the overlapping portion 700 and the other end of the supply check valve 71 is reduced.

When the flow rate of the hydraulic oil flowing through the supply flow path section 501 becomes a predetermined value or more, the outer peripheral wall of the supply check valve 71 contacts the stopper surface 42. Thereby, the supply check valve 71 is restricted from being deformed radially outward. At this time, a gap S1 is formed between the outer peripheral wall of the axial end portion of the supply check valve 71 and the stopper step surface 43 (see FIG. 7).

On the other hand, when the flow rate of the hydraulic oil flowing through the supply flow path section 501 becomes equal to or less than a predetermined value, the supply check valve 71 is deformed so as to shrink inward in the radial direction, that is, to reduce the inner diameter. Further, when hydraulic oil flows from the axial flow path portion 502 toward the supply flow path portion 501, the outer peripheral wall of the supply check valve 71 is pushed radially inward by the hydraulic oil, and the valve portion 701 contacts the valve seat surface 52. Touch. Thereby, the flow of the hydraulic oil from the axial direction flow path part 502 side to the supply flow path part 501 side is regulated. At this time, the supply check valve 71 is deformed so that the outer peripheral wall is located on the radially inner side of the inner sleeve 50 with respect to the valve seat step surface 53.

In this way, the supply check valve 71 functions as a check valve, allows hydraulic oil to flow from the supply flow path portion 501 side to the axial flow path portion 502 side, and is supplied from the axial flow path portion 502 side. The flow of the hydraulic oil to the flow path part 501 side can be regulated.

The movement restricting portion 56 is formed on the locking portion 59 side with respect to the supply check valve 71 in the circumferential flow path portion 503. The movement restricting portion 56 can restrict the movement of the supply check valve 71 toward the engaging portion 59 in the axial direction when it contacts the end of the supply check valve 71 in the axial direction.
The movement restricting portion 57 is formed on the side opposite to the locking portion 59 with respect to the supply check valve 71 in the circumferential flow path portion 503. The movement restricting portion 57 can restrict the movement of the supply check valve 71 to the side opposite to the axially engaging portion 59 when abutting against the end portion of the supply check valve 71 in the axial direction.

Thus, the

movement restricting portions

56 and 57 can prevent the supply check valve 71 from moving away from the supply flow path portion 501 in the axial direction. Further, the movement restricting portion 56 can prevent the supply check valve 71 from moving to the other side of the axial flow passage portion 502 and closing the radial flow passage portion 504.

The spool 60 includes a supply oil passage 601, a first control oil passage 611, a second control oil passage 612, a drain oil passage 602, and a recycle oil passage 603.
The supply oil passage 601 is formed in a substantially cylindrical shape so as to be recessed radially inward from the outer peripheral wall on one end side of the spool 60 and extending in the circumferential direction. The supply oil passage 601 is connected to the radial flow passage portion 504. Thus, the supply oil passage 601 communicates with the supply flow passage portion 501 via the axial flow passage portion 502. Therefore, hydraulic oil is supplied to the supply oil passage 601 from the oil pump 8 via the supply flow passage portion 501, the axial flow passage portion 502, and the radial flow passage portion 504.

The first control oil passage 611 is formed so as to penetrate the inner sleeve 50 in the radial direction. That is, the first control oil passage 611 connects the internal space 600 of the spool 60 and the outside. The first control oil passage 611 is formed integrally with the supply oil passage 601. Therefore, the supply oil passage 601 communicates with the internal space 600 of the spool 60 via the first control oil passage 611. Therefore, hydraulic oil can flow into the internal space 600 via the supply oil passage 601 and the first control oil passage 611.

The second control oil passage 612 is formed so as to penetrate the inner sleeve 50 in the radial direction. That is, the second control oil passage 612 connects the internal space 600 of the spool 60 and the outside. The second control oil passage 612 is formed on the sealing portion 62 side with respect to the first control oil passage 611.

The drain oil passage 602 is formed between the first control oil passage 611 and the second control oil passage 612 in the axial direction of the spool 60 so as to be recessed radially inward from the outer peripheral wall of the spool 60.

The recycle oil passage 603 is formed so as to penetrate the spool 60 in the radial direction in the drain oil passage 602. That is, the recycle oil passage 603 connects the internal space 600 of the spool 60 and the drain oil passage 602.

A first control port 411 and a second control port 412 are formed in the outer sleeve 40 and the inner sleeve 50.
The first control port 411 is formed so as to penetrate the outer sleeve 40 and the inner sleeve 50 in the radial direction on the locking portion 49 side with respect to the axial flow path portion 502. One end of the first control port 411 is connected to the space inside the inner sleeve 50. The other end of the first control port 411 is connected to the retard chamber 201 via the retard oil passage 301.

The second control port 412 is formed to penetrate the outer sleeve 40 and the inner sleeve 50 in the radial direction on the locking portion 49 side with respect to the first control port 411. One end of the second control port 412 is connected to the space inside the inner sleeve 50. The other end of the second control port 412 is connected to the advance chamber 202 via the advance oil passage 302.

A linear solenoid 9 is provided on the opposite side of the spool 60 from the cam shaft 3. The linear solenoid 9 is provided so as to contact the sealing portion 62. The linear solenoid 9 presses the spool 60 toward the camshaft 3 against the biasing force of the spring 63 through the sealing portion 62 by energization. Thereby, the axial position of the spool 60 with respect to the inner sleeve 50 changes. The movable range of the spool 60 is from a position where the spool 60 abuts on the locking portion 59 to a position where the spool 60 abuts on the sleeve plate portion 51.
The supply oil path 601 communicates with the radial flow path portion 504 regardless of the position of the spool 60 in the axial direction with respect to the inner sleeve 50.

The first control oil passage 611 and the first control port 411 are connected when the spool 60 is in a position where it abuts against the locking portion 59. At this time, the second control port 412 is connected to the drain oil passage 602 and the recycle oil passage 603. Further, the second control oil passage 612 and the second control port 412 are disconnected.

On the other hand, when the spool 60 contacts the sleeve plate portion 51, the second control oil passage 612 and the second control port 412 are connected. At this time, the first control port 411 is connected to the drain oil passage 602 and the recycle oil passage 603. Further, the first control oil passage 611 and the first control port 411 are disconnected.

Further, when the spool 60 is at an intermediate position between the locking portion 59 and the sleeve plate portion 51, the first control oil passage 611, the second control oil passage 612, the drain oil passage 602, the recycle oil passage 603, and the first control port. 411 and the second control port 412 are disconnected. At this time, the retard chamber 201 and the advance chamber 202 are closed.

As described above, the spool 60 connects and disconnects the first control oil passage 611 and the second control oil passage 612 and the first control port 411 and the second control port 412 according to the position in the axial direction with respect to the inner sleeve 50. Switching is possible.

Further, when the spool 60 is in contact with the locking portion 59, the other end of the axial flow passage portion 502 is the radial flow passage portion 504, the supply oil passage 601, the first control oil passage 611, and the first control port. It is connected to the retarding angle chamber 201 via 411.

When the spool 60 comes into contact with the sleeve plate portion 51, the other end of the axial flow passage portion 502 is connected to the radial flow passage portion 504, the supply oil passage 601, the first control oil passage 611, the internal space 600, and the second. The control oil passage 612 and the second control port 412 are connected to the advance chamber 202.

Thus, the other end side of the axial flow path portion 502 can be connected to the retard chamber 201 or the advance chamber 202 of the valve timing adjusting device 10 via the radial flow path portion 504.

In the present embodiment, a breathing hole 505 and a drain port 506 are formed in the inner sleeve 50.
The breathing hole 505 is formed so as to be recessed radially inward from the outer peripheral wall of the inner sleeve 50 and extend in the axial direction of the inner sleeve 50 (see FIGS. 3 and 6). Further, the breathing hole 505 has one end connected to the variable volume space 500 and the other end communicating with the outside, that is, the atmosphere via the engagement portion 59 and the sealing portion 62. Thereby, the pressure of the volume variable space 500 can be made equal to atmospheric pressure. Therefore, the axial movement of the spool 60 can be made smooth.

The drain port 506 is formed so as to connect the space inside the inner sleeve 50 and the breathing hole 505. The end of the drain port 506 opposite to the breathing hole 505 is connected to the drain oil passage 602 regardless of the position of the spool 60 in the axial direction with respect to the inner sleeve 50. As a result, the hydraulic oil in the drain oil passage 602 can flow out of the hydraulic oil control valve 11 via the drain port 506, the breathing hole 505, and between the locking part 59 and the sealing part 62.

In the present embodiment, the hydraulic oil control valve 11 further includes a recycle check valve 81.
The recycle check valve 81 is provided in the internal space 600 of the spool 60.
The recycle check valve 81 is formed, for example, by bending a thin metal plate. FIG. 8 is a developed view of the recycle check valve 81. FIG. 3 shows the recycle check valve 81 viewed from the direction perpendicular to the axis.

The recycle check valve 81 has a shaft portion 811 and a valve portion 812.
The shaft portion 811 is formed in a substantially cylindrical shape. The valve portion 701 is formed so as to extend from one end in the circumferential direction of the shaft portion 811 at the center of the shaft portion 811 so as to make one turn around the shaft portion 811. An end portion of the valve portion 701 opposite to the shaft portion 811 in the circumferential direction overlaps the radially outer side of the valve portion 812.

The recycle check valve 81 is provided in the internal space 600 so that the valve portion 812 corresponds to the recycle oil passage 603. Here, the end portion of the shaft portion 811 is in contact with the spool plate portion 61 and the sealing portion 62, and movement in the axial direction is restricted.
In the recycle check valve 81, the valve portion 812 blocks the recycle oil passage 603 in the internal space 600. In the recycle check valve 81, the valve portion 812 is elastically deformable in the radial direction.

When hydraulic oil flows from the recycle oil path 603 side to the internal space 600 side, the recycle check valve 81 is configured so that the outer wall of the valve portion 812 is pushed by the hydraulic oil and contracts radially inward, that is, the inner diameter decreases. And deform. As a result, the valve portion 812 is separated from the recycle oil passage 603, and the hydraulic oil can flow into the internal space 600 and flow between the valve portion 812 and the inner peripheral wall of the spool 60. At this time, the overlapping area of the end portions in the circumferential direction of the valve portion 812 increases.

On the other hand, when the hydraulic oil flows from the internal space 600 side to the recycle oil passage 603 side, the recycle check valve 81 is pushed by the hydraulic oil to the inner wall of the valve portion 812 and expands radially outward, that is, the inner diameter increases. It deforms like this. As a result, the valve portion 812 blocks the recycle oil passage 603 and the flow of hydraulic oil from the internal space 600 to the recycle oil passage 603 is blocked.

Thus, the recycle check valve 81 functions as a check valve, allows the flow of hydraulic oil from the recycle oil path 603 side to the internal space 600 side, and operates from the internal space 600 side to the recycle oil path 603 side. Oil flow can be regulated.

Next, the operation of the hydraulic oil control valve 11 and the valve timing adjusting device 10 will be described. The hydraulic oil control valve 11 presses the spool 60 by driving the linear solenoid 9 and connects the advance chamber 202 to the drain oil passage 602 and the recycle oil passage 603 while connecting the oil pump 8 and the retard chamber 201. A first operating state, a second operating state in which the retard chamber 201 is connected to the drain oil passage 602 and the recycled oil passage 603 while the oil pump 8 and the advance chamber 202 are connected, and the retard chamber 201 and It operates to a holding state in which the advance chamber 202 is closed together.

In the first operation state, while the hydraulic oil is supplied to the retard chamber 201, the hydraulic oil is returned from the advance chamber 202 to the internal space 600 via the drain oil passage 602 and the recycle oil passage 603, and the surplus portion is drained. The oil is discharged to the outside of the hydraulic oil control valve 11 through the port 506 and the breathing hole 505 and returned to the oil pan 7. In the second operation state, while the hydraulic oil is supplied to the advance chamber 202, the hydraulic oil is returned from the retard chamber 201 to the internal space 600 via the drain oil passage 602 and the recycle oil passage 603, and the surplus portion is drained. The oil is discharged to the outside of the hydraulic oil control valve 11 through the port 506 and the breathing hole 505 and returned to the oil pan 7. In the hold state, the hydraulic oil in the retard chamber 201 and the advance chamber 202 is held.

The present embodiment further includes a lock pin 33 (see FIGS. 1 and 2). The lock pin 33 is formed in a bottomed cylindrical shape, and is housed in a housing hole 321 formed in the vane 32 so as to be capable of reciprocating in the axial direction. A spring 34 is provided inside the lock pin 33. The spring 34 biases the lock pin 33 toward the bottom side of the case 22. A fitting recess 25 is formed on the bottom of the case 22 on the vane 32 side.

The lock pin 33 can be inserted into the insertion recess 25 when the vane rotor 30 is at the most retarded position with respect to the housing 20. When the lock pin 33 is fitted in the fitting recess 25, relative rotation of the vane rotor 30 with respect to the housing 20 is restricted. On the other hand, when the lock pin 33 is not inserted into the insertion recess 25, relative rotation of the vane rotor 30 with respect to the housing 20 is allowed.

A pin control oil passage 304 communicating with the advance chamber 202 is formed between the lock pin 33 of the vane 32 and the advance chamber 202 (see FIG. 2). The pressure of the hydraulic oil flowing into the pin control oil passage 304 from the advance chamber 202 acts in a direction in which the lock pin 33 comes out of the fitting recess 25 against the urging force of the spring 34.

In the valve timing adjusting device 10 configured as described above, when hydraulic oil is supplied to the advance chamber 202, the hydraulic oil flows into the pin control oil passage 304, and the lock pin 33 comes out of the fitting recess 25, and the housing The relative rotation of the vane rotor 30 with respect to 20 is permitted.

When the rotational phase of the camshaft 3 is on the more advanced side than the target value, the valve timing adjusting device 10 sets the hydraulic oil control valve 11 to the first operating state. As a result, the vane rotor 30 rotates relative to the housing 20 in the retarding direction, and the rotational phase of the camshaft 3 changes toward the retarding side.
Further, the valve timing adjusting device 10 places the hydraulic oil control valve 11 in the second operating state when the rotational phase of the camshaft 3 is retarded from the target value. As a result, the vane rotor 30 rotates relative to the housing 20 in the advance direction, and the rotational phase of the camshaft 3 changes toward the advance side.
Further, the valve timing adjusting device 10 places the hydraulic oil control valve 11 in the holding state when the rotational phase of the camshaft 3 matches the target value. Thereby, the rotational phase of the cam shaft 3 is maintained.
In the present embodiment, part of the hydraulic oil from the retard chamber 201 and the advance chamber 202 can be reused by the recycle oil passage 603.

Further, in this embodiment, the pressure of the variable volume space 500 is equal to the atmospheric pressure by the breathing hole 505, so that when the linear solenoid 9 presses the spool 60, the spool 60 is located inside the inner sleeve 50. Can smoothly reciprocate in the axial direction. When the hydraulic oil is accumulated in the variable volume space 500, the hydraulic oil passes through the breathing hole 505 and is opposite to the hydraulic oil control valve 11 from the camshaft 3, that is, the valve timing adjusting device 10. It is discharged to the outside and returned to the oil pan 7.

When the oil pump 8 is operated when the hydraulic oil control valve 11 is in the first operating state or the second operating state, the hydraulic oil flows into the axial channel portion 502 via the supply channel portion 501. At this time, the supply check valve 71 is separated from the valve seat surface 52, that is, is opened to allow the flow of hydraulic oil. If the flow rate of the hydraulic oil at this time is large, the supply check valve 71 is further deformed radially outward and comes into contact with the stopper surface 42. At this time, the hydraulic oil can smoothly flow in the axial direction from the supply flow path portion 501 to the axial flow path portion 502 without being blocked by the supply check valve 71. Here, in the case where the oil in the retard chamber 201 or the advance chamber 202 is compressed by the action of torque transmitted from the camshaft 3 and the pressure rises, the supply channel section 501 and the axial channel section 502 Hydraulic fluid may flow backward. Here, the “back flow” means flowing from the axial flow path portion 502 side to the supply flow path portion 501 side. same as below.

When the hydraulic oil flows backward with the supply check valve 71 in contact with the stopper surface 42, the hydraulic oil enters the gap S1 between the supply check valve 71 and the stopper step surface 43, and the outer wall of the supply check valve 71 is in the radial direction. It is pushed inward. Thereby, the supply check valve 71 can be closed quickly.

In the present embodiment, the valve seat step surface 53 is formed on the radially outer side of the inner sleeve 50 with respect to the valve seat surface 52, and the supply check valve 71 has an outer peripheral wall when no external force is applied. Is located on substantially the same plane as the valve seat step surface 53. When the supply check valve 71 is in this state and hydraulic fluid flows backward, the hydraulic oil in the axial flow path portion 502 does not enter between the inner wall of the supply check valve 71 and the valve seat surface 52, and the supply check valve 71. Push the outer wall of the inside in the radial direction. Thereby, the supply check valve 71 can be closed quickly.

Further, in this embodiment, the

movement restricting portions

56 and 57 can prevent the supply check valve 71 from moving in the axial direction and leaving the supply flow path portion 501. Further, the movement restricting section 56 can prevent the supply check valve 71 from moving to the other side of the axial flow path section 502 and closing the radial flow path section 504.

As described above, the present embodiment is the hydraulic oil control valve 11 that can control the flow of hydraulic oil supplied from the oil pump 8 to the valve timing adjusting device 10, and includes the outer sleeve 40, the inner sleeve 50, and the supply flow. A passage portion 501, an axial flow passage portion 502, and a supply check valve 71 are provided.
The outer sleeve 40 is formed in a cylindrical shape.
The inner sleeve 50 is formed in a cylindrical shape and is provided inside the outer sleeve 40.
The supply flow path portion 501 is formed so as to penetrate the inner sleeve 50 in the radial direction, and the hydraulic oil from the oil pump 8 flows.
The axial flow path portion 502 is formed so as to extend in the axial direction between the outer sleeve 40 and the inner sleeve 50, the supply flow path portion 501 opens at one end side, and the other end side can be connected to the valve timing adjusting device 10. It is.
The supply check valve 71 is provided radially outside the inner sleeve 50 with respect to the supply flow path section 501 in the axial flow path section 502, and supplies hydraulic oil from the supply flow path section 501 side to the axial flow path section 502 side. The flow is allowed, and the flow of hydraulic oil from the axial flow path portion 502 side to the supply flow path portion 501 side can be regulated.

In the present embodiment, the hydraulic oil that has flowed from the supply flow path portion 501 to the axial flow path portion 502 flows to the other end side of the axial flow path portion 502 without bypassing the supply check valve 71, thereby adjusting the valve timing. Supplied to the apparatus 10. Therefore, the flow path pressure loss in the hydraulic oil control valve 11 can be suppressed. Thereby, the responsiveness of the valve timing adjusting device 10 can be improved.

Further, in this embodiment, even if a large amount of hydraulic oil flows from the supply flow path portion 501 to the axial flow path portion 502, the supply check valve 71 contacts the wall surface facing the opening of the supply flow path portion 501. However, the axial flow path portion 502 is not blocked. Therefore, the unintended flow path interruption in the hydraulic oil control valve 11 can be suppressed.

The present embodiment further includes

movement restricting portions

56 and 57 that can restrict the movement of the supply check valve 71 in the axial direction. Therefore, it is possible to prevent the supply check valve 71 from moving in the axial direction and leaving the supply flow path portion 501. Thereby, the state in which the supply check valve 71 functions as a check valve can be maintained.

In addition, the present embodiment further includes a circumferential flow path portion 503. The circumferential flow path portion 503 is formed in an annular shape between the outer sleeve 40 and the inner sleeve 50, extending in the circumferential direction from one end of the axial flow path portion 502.
The supply check valve 71 is formed in a cylindrical shape, and is provided so as to be elastically deformable in the radial direction at one end of the axial flow path portion 502 and the circumferential flow path portion 503.
The axial flow path portion 502 is formed around the opening of the supply flow path portion 501 and at a position facing the valve seat surface 52 on which the supply check valve 71 can contact and the opening of the supply flow path portion 501. It has a stopper surface 42 that can regulate the deformation of the supply check valve 71 in the radial direction when the supply check valve 71 comes into contact.
In the present embodiment, the circumferential flow path portion 503 and the supply check valve 71 can be formed relatively easily. Further, by forming the stopper surface 42 as described above, the deformation of the supply check valve 71 can be restricted without hindering the flow of hydraulic oil.

In the present embodiment, the axial flow path portion 502 is a valve formed on the other end side of the axial flow path portion 502 with respect to the valve seat surface 52 and on the radially outer side of the inner sleeve 50 with respect to the valve seat surface 52. A seat step surface 53 is provided. Therefore, the supply check valve 71 can be positioned with the outer wall substantially flush with the valve seat step surface 53 or on the valve seat surface 52 side. When the supply check valve 71 is in this state and hydraulic fluid flows backward, the hydraulic oil in the axial flow path portion 502 does not enter the supply check valve 71 and pushes the outer wall of the supply check valve 71 radially inward. . Thereby, the supply check valve 71 can be closed quickly. That is, the valve seat step surface 53 can suppress the occurrence of a flow that hinders the closing of the supply check valve 71.

In the present embodiment, the axial flow path portion 502 is a stopper step surface formed on the radially outer side of the outer sleeve 40 with respect to the stopper surface 42 on the other end side of the axial flow path portion 502 with respect to the stopper surface 42. 43.

In the present embodiment, the boundary between the stopper surface 42 and the stopper step surface 43 is located within the range of the axial length of the supply check valve 71. Therefore, when the supply check valve 71 abuts against the stopper surface 42 and deformation is restricted, a gap S 1 is formed between the outer wall of the supply check valve 71 and the stopper step surface 43. Accordingly, when the hydraulic oil flows backward at this time, the hydraulic oil enters the gap S1, and the outer wall of the supply check valve 71 is pushed inward in the radial direction. Thereby, the supply check valve 71 can be closed quickly.

In addition, the present embodiment further includes a radial flow path portion 504. The radial flow path portion 504 is formed so as to penetrate the inner sleeve 50 in the radial direction, and has one end connected to the other end side of the axial flow path portion 502 and the other end side connectable to the valve timing adjusting device 10. The hydraulic fluid in the axial flow path portion 502 can be caused to flow inside the inner sleeve 50 by the radial flow path portion 504.
In addition, since this embodiment is provided with the movement control part 56, it can prevent that the supply check valve 71 moves to the other side of the axial direction flow-path part 502, and block | closes the radial direction flow-path part 504. As a result, unintended flow passage interruption in the hydraulic oil control valve 11 including the radial flow passage portion 504 can be suppressed.

In the present embodiment, the outer sleeve 40 has an inner peripheral wall formed in a cylindrical surface shape. The inner sleeve 50 has an outer peripheral wall formed in a cylindrical surface shape. The axial flow path portion 502 is formed on the fitting boundary surface T 1 between the outer sleeve 40 and the inner sleeve 50 so as to be recessed radially inward from the outer peripheral wall of the inner sleeve 50. Therefore, the fitting boundary surface T1 between the outer sleeve 40 and the inner sleeve 50 and the axial flow path portion 502 can be formed with high accuracy.

In the present embodiment, the outer sleeve 40 has a threaded portion 41 on the outer peripheral wall that can be screwed to the inner wall of the valve timing adjusting device 10. The inner sleeve 50 is formed of a material having a lower hardness than the outer sleeve 40. The axial flow path portion 502 and the

movement restriction portions

56 and 57 are formed in the inner sleeve 50. Therefore, it is possible to easily and accurately form the axial flow path portion 502 and the

movement restricting portions

56 and 57 on the inner sleeve 50 by cutting or the like while ensuring the strength of the screw portion 41 of the outer sleeve 40.

In the present embodiment, the outer sleeve 40 is made of a material containing iron. The inner sleeve 50 is formed of a material containing aluminum. This specifically shows the configuration of the inner sleeve 50 having a lower hardness than the outer sleeve 40. With this configuration, the axial flow path portion 502 and the like can be easily formed in the inner sleeve 50 while ensuring the strength of the outer sleeve 40.

In the present embodiment, the outer sleeve 40 and the inner sleeve 50 have a first control port 411 and a second control port 412 that are formed so as to be connected to the valve timing adjusting device 10. The present embodiment further includes a spool 60. The spool 60 is formed in a cylindrical shape so as to be reciprocally movable in the axial direction inside the inner sleeve 50, forms an internal space 600 on the inner side, and the internal space 600 and the other end side of the axial flow path portion 502. , And the first control oil path 611 and the second control oil path 612 formed to be connectable to the internal space 600 and the first control port 411 and the second control port 412. The first control oil passage 611, the second control oil passage 612, the first control port 411, and the second control port 412 can be switched between connection and disconnection according to the position with respect to the inner sleeve 50.
This shows a specific example when the hydraulic oil control valve 11 is used for control of the valve timing adjusting device 10. By switching connection and disconnection between each control oil passage and each control port by the spool 60, the valve timing adjusting device 10 can be changed into a plurality of states.

The present embodiment is provided in a power transmission path for transmitting power from the crankshaft 2 to the camshaft 3 of the engine 1 and adjusts the valve timings of the intake valve 4 and the exhaust valve 5 that are opened and closed by the camshaft 3. The adjusting device 10 includes a housing 20, a vane rotor 30, and the hydraulic oil control valve 11.
The housing 20 rotates in conjunction with the crankshaft 2, is fitted to the end of the camshaft 3, and is rotatably supported by the camshaft 3.
The vane rotor 30 is fixed to the end of the camshaft 3 and includes a vane 32 that divides the space 200 inside the housing 20 into a plurality of retarding chambers 201 and advancing chambers 202. From the oil pump 8 to the retarding chamber 201, It rotates relative to the housing 20 according to the pressure of the hydraulic oil supplied to the advance chamber 202.
The hydraulic oil control valve 11 can control the flow of hydraulic oil supplied from the oil pump 8 to the valve timing adjusting device 10.
The first control port 411 and the second control port 412 are connected to the retard chamber 201 and the advance chamber 202, respectively.
This shows a specific example when the hydraulic oil control valve 11 is applied to the valve timing adjusting device 10. The hydraulic oil control valve 11 of the present embodiment can suppress flow path pressure loss and suppress unintended flow path blockage, so that the valve timing adjusting device 10 is highly responsive, and is controlled efficiently and with high accuracy. be able to.

In the present embodiment, the hydraulic oil control valve 11 is provided in the central portion of the vane rotor 30. That is, the hydraulic oil control valve 11 and the valve timing adjusting device 10 are provided integrally. Therefore, the hydraulic oil control valve 11 and the valve timing adjusting device 10 can be arranged in a compact manner.

(Second Embodiment)
9 to 11 show a hydraulic oil control valve according to the second embodiment and a part thereof. The second embodiment differs from the first embodiment in the configuration of the outer sleeve 40, the inner sleeve 50, the spool 60, and the like.

In the second embodiment, the supply flow path portion 401 is formed in the outer sleeve 40. The supply channel portion 501 is formed so as to penetrate the outer sleeve 40 in the radial direction on the locking portion 49 side with respect to the screw portion 41. For example, four supply flow path portions 401 are formed at equal intervals in the circumferential direction of the outer sleeve 40. The hydraulic oil from the oil pump 8 flows through the supply channel 401.

The axial flow path portion 502 is formed to extend in the axial direction between the outer sleeve 40 and the inner sleeve 50.
The axial flow path portion 502 is formed on the fitting boundary surface T 1 between the outer sleeve 40 and the inner sleeve 50 so as to be recessed radially inward from the outer peripheral wall of the inner sleeve 50.
In the present embodiment, four axial flow path portions 502 are formed at equal intervals in the circumferential direction of the inner sleeve 50 (see FIG. 10).

Each of the four supply flow channel portions 401 connects one end side of each of the four axial flow channel portions 502 and the outside of the outer sleeve 40. That is, the supply flow path portion 401 is open on one end side of the axial flow path portion 502.

The circumferential flow path portion 503 is formed in an annular shape between the outer sleeve 40 and the inner sleeve 50, extending in the circumferential direction from one end of the axial flow path portion 502 (see FIGS. 9 to 11). That is, four supply flow path portions 401 are opened in the circumferential flow path portion 503. The circumferential flow path portion 503 is connected to one end of the four axial flow path portions 502.
The hydraulic oil from the oil pump 8 can flow into the axial flow path portion 502 and the circumferential flow path portion 503 via the supply flow path portion 401.

The radial flow path portion 504 is formed so as to penetrate the inner sleeve 50 in the radial direction, and has one end connected to the other end side of the axial flow path portion 502 and the other end side connected to a space inside the inner sleeve 50. (See FIGS. 9 to 11). Four radial flow path portions 504 are formed so as to be connected to each of the four axial flow path portions 502 (see FIG. 10).

The supply check valve 71 has the same configuration as in the first embodiment.
The supply check valve 71 is provided in the circumferential flow path portion 503. The supply check valve 71 is provided so as to be elastically deformable in the radial direction at one end of the axial flow path portion 502 and the circumferential flow path portion 503. Here, the supply check valve 71 is provided so that the four valve parts 701 correspond to the four supply flow path parts 401, respectively. That is, the supply check valve 71 is provided on the radially inner side of the outer sleeve 40 with respect to the supply flow path portion 401.

The axial flow path portion 502 has a valve seat surface 44, a valve seat step surface 45, a stopper surface 54, and a stopper step surface 55.
The valve seat surface 44 is formed in an annular shape around the opening of the supply flow path portion 401 in the outer sleeve 40, and can contact the valve portion 701 of the supply check valve 71. The valve seat step surface 45 is formed on the radially inner side of the outer sleeve 40 with respect to the valve seat surface 44 on the other end side of the axial flow path portion 502 with respect to the valve seat surface 44 (see FIG. 11).

The stopper surface 54 is formed in the inner sleeve 50 at a position facing the opening of the supply flow path portion 401. The stopper step surface 55 is formed on the radially inner side of the inner sleeve 50 with respect to the stopper surface 54 on the other end side of the axial flow path portion 502 with respect to the stopper surface 54 (see FIG. 11).

The supply check valve 71 is provided in the circumferential flow path portion 503, and in a state where hydraulic fluid does not flow through the supply flow path portion 401, that is, in a state where no external force is applied, the inner peripheral wall is the valve seat step surface 45. Are located on substantially the same plane (see FIG. 11).
Here, the boundary B1 between the stopper surface 54 and the stopper step surface 55 is located within the range of the axial length of the supply check valve 71 (see FIG. 11).

When the hydraulic oil flows to the axial flow channel portion 502 and the circumferential flow channel portion 503 via the supply flow channel portion 401, the supply check valve 71 is radially inward because the outer wall of the valve portion 701 is pushed by the hydraulic fluid. It deforms to shrink, that is, to reduce the inner diameter. As a result, the valve portion 701 of the supply check valve 71 is separated from the valve seat surface 44, and the hydraulic oil passes between the valve portion 701 and the valve seat surface 44, and the other end portion of the axial flow passage portion 502. It can flow to the side, that is, the radial flow path portion 504 side.

When the flow rate of the hydraulic oil flowing through the supply flow path portion 401 becomes a predetermined value or more, the inner peripheral wall of the supply check valve 71 contacts the stopper surface 54. Thereby, the supply check valve 71 is restricted from being deformed radially inward. At this time, a gap S1 is formed between the inner peripheral wall of the axial end of the supply check valve 71 and the stopper step surface 55 (see FIG. 11).

On the other hand, when the flow rate of the hydraulic oil flowing through the supply flow path unit 401 becomes a predetermined value or less, the supply check valve 71 is deformed so as to expand outward in the radial direction, that is, to increase the inner diameter. Further, when hydraulic fluid flows from the axial flow channel portion 502 toward the supply flow channel portion 401, the inner peripheral wall of the supply check valve 71 is pushed radially outward by the hydraulic fluid, and the valve portion 701 contacts the valve seat surface 44. Touch. Thereby, the flow of the hydraulic oil from the axial direction flow path part 502 side to the supply flow path part 401 side is regulated. At this time, the supply check valve 71 is deformed so that the inner peripheral wall is located on the radially outer side of the outer sleeve 40 with respect to the valve seat step surface 45.

In this way, the supply check valve 71 functions as a check valve, allows hydraulic oil to flow from the supply flow path portion 401 side to the axial flow passage portion 502 side, and is supplied from the axial flow passage portion 502 side. It is possible to regulate the flow of hydraulic oil to the flow path portion 401 side.

The movement restricting portion 56 is formed on the side opposite to the locking portion 59 with respect to the supply check valve 71 in the circumferential flow path portion 503. The movement restricting portion 56 can restrict the movement of the supply check valve 71 to the side opposite to the axially engaging portion 59 when contacting the end portion of the supply check valve 71 in the axial direction.
The movement restricting portion 57 is formed on the locking portion 59 side with respect to the supply check valve 71 in the circumferential flow path portion 503. The movement restricting portion 57 can restrict the movement of the supply check valve 71 toward the engaging portion 59 in the axial direction when it contacts the end of the supply check valve 71 in the axial direction.

As described above, the

movement restricting portions

56 and 57 can prevent the supply check valve 71 from moving in the axial direction and leaving the supply flow path portion 401. Further, the movement restricting portion 56 can prevent the supply check valve 71 from moving to the other side of the axial flow passage portion 502 and closing the radial flow passage portion 504.

In the present embodiment, the sleeve plate portion 51 is formed so as to block one end portion of the inner sleeve 50 (see FIG. 9). A breathing hole portion 507 is formed in the sleeve plate portion 51. The breathing hole 507 connects the variable volume space 500 and the outside of the hydraulic oil control valve 11, that is, the atmosphere. Thereby, the pressure of the variable volume space 500 can be made equal to the atmospheric pressure, and the axial movement of the spool 60 can be made smooth.

In the present embodiment, the supply oil passage 601 is formed in a substantially cylindrical shape so as to be recessed radially inward from the outer peripheral wall on one end side of the spool 60 and extending in the circumferential direction. One end of the supply oil passage 601 is connected to the radial flow path portion 504. As a result, the supply oil passage 601 communicates with the supply passage portion 401 via the axial passage portion 502. Therefore, hydraulic oil is supplied to the supply oil passage 601 from the oil pump 8 via the supply passage portion 401, the axial passage portion 502, and the radial passage portion 504.

The first control oil passage 611 is formed so as to penetrate the inner sleeve 50 in the radial direction. The first control oil passage 611 is formed integrally with the supply oil passage 601. Therefore, the supply oil passage 601 communicates with the internal space 600 of the spool 60 via the first control oil passage 611. Therefore, hydraulic oil can flow into the internal space 600 via the supply oil passage 601 and the first control oil passage 611.

The configurations of the second control oil passage 612, the drain oil passage 602, the recycle oil passage 603, the first control port 411, and the second control port 412 are the same as those in the first embodiment, and thus the description thereof is omitted.
Further, the connection and disconnection between the control oil passages and the control ports by the spool 60 are the same as in the first embodiment, and thus the description thereof is omitted.

Since the configuration and arrangement of the recycle check valve 81 are the same as those in the first embodiment, description thereof is omitted.
In the present embodiment, a drain hole 508 is formed in the inner sleeve 50 instead of the breathing hole 505. The drain hole 508 is formed so as to be recessed radially inward from the outer peripheral wall of the inner sleeve 50 and extend in the axial direction of the inner sleeve 50 (see FIG. 9). Further, the drain hole 508 has a drain port 506 opened on one end side, and the other end communicated with the outside, that is, the atmosphere via a gap between the locking portion 59 and the sealing portion 62. Thereby, the hydraulic oil can be discharged to the outside of the hydraulic oil control valve 11 via the drain port 506 and the drain hole 508.

In the present embodiment, when the oil pump 8 is operated when the hydraulic oil control valve 11 is in the first operating state or the second operating state, the hydraulic oil is supplied to the axial channel portion 502 via the supply channel portion 401. Flowing. At this time, the supply check valve 71 is separated from the valve seat surface 44, that is, is opened to allow the flow of hydraulic oil. When the flow rate of the hydraulic oil at this time is large, the supply check valve 71 is further deformed radially inward and comes into contact with the stopper surface 54. At this time, the hydraulic oil can smoothly flow in the axial direction from the supply flow path section 401 to the axial flow path section 502 without being blocked by the supply check valve 71. Here, when the oil pump 8 is stopped, the hydraulic fluid may flow backward in the supply flow path portion 401 and the axial flow path portion 502.

When the hydraulic oil flows backward with the supply check valve 71 in contact with the stopper surface 54, the hydraulic oil enters the gap S 1 between the supply check valve 71 and the stopper step surface 55, and the inner wall of the supply check valve 71 is in the radial direction. Pushed outward. Thereby, the supply check valve 71 can be closed quickly.

Further, in the present embodiment, the valve seat step surface 45 is formed on the inner side in the radial direction of the outer sleeve 40 with respect to the valve seat surface 44, and the supply check valve 71 has an inner peripheral wall when no external force is applied. Is located on substantially the same plane as the valve seat step surface 45. When the supply check valve 71 is in this state and hydraulic fluid flows backward, the hydraulic oil in the axial flow path portion 502 does not enter between the outer wall of the supply check valve 71 and the valve seat surface 44, and the supply check valve 71. Push the inner wall of the outer side in the radial direction. Thereby, the supply check valve 71 can be closed quickly.

Further, in this embodiment, the

movement restricting portions

As described above, in the present embodiment, the supply flow path portion 401 is formed so as to penetrate the outer sleeve 40 in the radial direction, and the hydraulic oil from the oil pump 8 flows. The axial flow path portion 502 is formed to extend in the axial direction between the outer sleeve 40 and the inner sleeve 50, the supply flow path portion 401 is opened at one end side, and the other end side can be connected to the valve timing adjusting device 10. It is. The supply check valve 71 is provided on the radially inner side of the outer sleeve 40 with respect to the supply flow path section 401 in the axial flow path section 502, and the hydraulic oil is supplied from the supply flow path section 401 side to the axial flow path section 502 side. The flow is allowed and the flow of hydraulic oil from the axial flow path portion 502 side to the supply flow path portion 401 side can be regulated.
In the present embodiment, the hydraulic oil that has flowed from the supply flow path portion 401 to the axial flow path portion 502 flows to the other end side of the axial flow path portion 502 without bypassing the supply check valve 71, thereby adjusting the valve timing. Supplied to the apparatus 10. Therefore, the flow path pressure loss in the hydraulic oil control valve 11 can be suppressed. Thereby, the responsiveness of the valve timing adjusting device 10 can be improved.
Even if a large amount of hydraulic oil flows from the supply flow path portion 501 to the axial flow path portion 502, the supply check valve 71 only abuts against the wall surface facing the opening of the supply flow path portion 401. The direction flow path portion 502 is not blocked. Therefore, the unintended flow path interruption in the hydraulic oil control valve 11 can be suppressed.

Further, in the present embodiment, the axial flow path portion 502 is formed around the opening of the supply flow path portion 401, the valve seat surface 44 with which the supply check valve 71 can come into contact, and the opening of the supply flow path portion 401. The stopper surface 54 is formed at a position opposite to the supply check valve 71 and is capable of restricting radial deformation of the supply check valve 71 when the supply check valve 71 comes into contact therewith.
In the present embodiment, by forming the stopper surface 54 as described above, the deformation of the supply check valve 71 can be regulated without hindering the flow of hydraulic oil.

In the present embodiment, the axial flow passage portion 502 is a valve formed on the other end side of the axial flow passage portion 502 with respect to the valve seat surface 44 and radially inward of the outer sleeve 40 with respect to the valve seat surface 44. A seat step surface 45 is provided. Therefore, the same effect as that of the first embodiment can be obtained.

In the present embodiment, the axial flow path portion 502 is a stopper step surface formed on the radially outer side of the outer sleeve 40 with respect to the stopper surface 42 on the other end side of the axial flow path portion 502 with respect to the stopper surface 42. 43. Therefore, the same effect as that of the first embodiment can be obtained.

(Third embodiment)
A part of the hydraulic oil control valve according to the third embodiment is shown in FIG. The third embodiment is different from the second embodiment in the configuration of the inner sleeve 50 and the like.

The second embodiment further includes a valve closing assist flow path section 509. The valve closing assist flow path portion 509 is formed so as to penetrate the inner sleeve 50 in the radial direction and open at one end to the stopper surface 54. The hydraulic oil in the supply oil passage 601 can flow inside the valve closing assist flow passage portion 509.

In the present embodiment, when a reverse flow occurs when the outer wall of the supply check valve 71 is pushed by the hydraulic oil and the inner wall is in contact with the stopper surface 54, the inner wall of the supply check valve 71 operates in the valve closing assist channel 509. Pushed by the oil, the supply check valve 71 is deformed radially outward and closes. As described above, the valve closing assist flow path section 509 assists in closing the supply check valve 71.

As described above, the present embodiment further includes the valve closing assist channel portion 509. The valve closing assist flow passage portion 509 is formed so as to penetrate the inner sleeve 50 in the radial direction, one end thereof opens to the stopper surface 54, and hydraulic oil can flow into the inner side. The valve closing assist channel 509 can assist in closing the supply check valve 71.

(Fourth embodiment)
The hydraulic oil control valve according to the fourth embodiment is shown in FIG. The fourth embodiment differs from the second embodiment in the configuration of the inner sleeve 50 and the like.

In the fourth embodiment, the inner sleeve 50 includes a first inner sleeve 511 and a second inner sleeve 512.

The first inner sleeve 511 is formed in a substantially cylindrical shape by a material having a relatively low hardness such as a resin. That is, the first inner sleeve 511 is formed of a material having a lower hardness than the outer sleeve 40.

The second inner sleeve 512 is formed in a substantially cylindrical shape with a material having relatively high hardness including, for example, iron. That is, the second inner sleeve 512 is formed of a material having a hardness higher than that of the first inner sleeve 511.

The first inner sleeve 511 is provided inside the outer sleeve 40 so that the outer peripheral wall is fitted to the inner peripheral wall of the outer sleeve 40. The first inner sleeve 511 is not movable relative to the outer sleeve 40.

The second inner sleeve 512 is provided inside the first inner sleeve 511 so that the outer peripheral wall is fitted to the inner peripheral wall of the first inner sleeve 511. The second inner sleeve 512 is not movable relative to the first inner sleeve 511.

The axial flow path portion 502 is formed to extend in the axial direction between the outer sleeve 40 and the first inner sleeve 511.
The axial flow path portion 502 is formed in the first inner sleeve 511 on the fitting interface T1 between the outer sleeve 40 and the first inner sleeve 511 so as to be recessed radially inward from the outer peripheral wall of the first inner sleeve 511. Yes.

The radial flow path portion 504 is formed so as to penetrate the second inner sleeve 512 in the radial direction, and one end is connected to the other end side of the axial flow path portion 502 and the other end side is connected to the space inside the inner sleeve 50. (See FIG. 13).

In the fourth embodiment, the

movement restricting portions

56 and 57 are formed on the first inner sleeve 511. The sleeve plate portion 51 is formed integrally with the first inner sleeve 511 so as to block one end portion of the first inner sleeve 511.
In the fourth embodiment, the valve seat step surface 45 and the stopper step surface 55 are not formed.

As described above, in the present embodiment, the outer sleeve 40 has the screw portion 41 that can be screwed to the inner wall of the valve timing adjusting device 10 on the outer peripheral wall.
The inner sleeve 50 is a cylindrical first inner sleeve 511 formed of a material having a lower hardness than the outer sleeve 40, and an inner side of the first inner sleeve 511 formed of a material having a higher hardness than the first inner sleeve 511. A cylindrical second inner sleeve 512 is provided. The axial flow path portion 502 is formed in the first inner sleeve 511. In the present embodiment, the axial flow path portion 502 and the

movement restricting portions

56 and 57 are formed in the first inner sleeve 511 having a lower hardness than the outer sleeve 40. Therefore, the axial flow path portion 502 and the

movement restricting portions

56 and 57 can be easily and accurately formed on the first inner sleeve 511 by cutting or the like while ensuring the strength of the screw portion 41 of the outer sleeve 40.
In addition, the second inner sleeve 512 having a higher hardness than the first inner sleeve 511 is formed in a substantially cylindrical simple shape. Therefore, the second inner sleeve 512 can be easily formed even if the hardness is high. Further, the strength of the second inner sleeve 512 on which the outer wall of the spool 60 slides on the inner wall can be ensured.

In the present embodiment, the outer sleeve 40 is made of a material containing iron. The first inner sleeve 511 is made of resin. The second inner sleeve 512 is formed of a material containing iron. This specifically illustrates the configuration of the outer sleeve 40, the first inner sleeve 511, and the second inner sleeve 512. With this configuration, the axial flow path portion 502 and the like can be easily formed in the first inner sleeve 511 while ensuring the strength of the outer sleeve 40 and the second inner sleeve 512.

(Fifth embodiment)
A part of the hydraulic oil control valve according to the fifth embodiment is shown in FIGS. The fifth embodiment differs from the first embodiment in the configuration of the supply check valve.

In the fifth embodiment, similarly to the supply check valve 71 of the first embodiment, the supply check valve 72 is formed in a substantially cylindrical shape by bending, for example, a rectangular metal thin plate so that the longitudinal direction is along the circumferential direction. FIG. 14 is a developed view of the supply check valve 72. FIG. 15 is a cross-sectional view of the supply check valve 72 at an intermediate position in the axial direction.

In the fifth embodiment, the supply check valve 72 includes an overlapping portion 700, an opening 720, a support portion 721, and a valve portion 701.
The overlapping portion 700 is formed at one end portion of the supply check valve 72 in the circumferential direction. The overlapping portion 700 is formed so as to overlap the radially outer side of the other end portion in the circumferential direction of the supply check valve 72 (see FIG. 15).

Four openings 720 are formed at equal intervals in the circumferential direction of the supply check valve 72.
The support portion 721 is formed to extend from the inner edge portion of each of the four openings 720 in the circumferential direction of the supply check valve 72.

The valve portion 701 is formed so as to be connected to the distal end portion of the support portion 721. Here, four valve portions 701 are formed at equal intervals in the circumferential direction of the supply check valve 72.

The supply check valve 72 is provided in the circumferential flow path portion 503. The supply check valve 72 includes a support portion 721 and a valve portion 701 that are elastically deformable in the radial direction at one end of the axial flow passage portion 502 and the circumferential flow passage portion 503. Here, the supply check valve 72 is provided so that the four valve parts 701 correspond to the four supply flow path parts 501 respectively. That is, the supply check valve 72 is provided on the radially outer side of the inner sleeve 50 with respect to the supply flow path portion 501.

(Sixth embodiment)
A part of the hydraulic oil control valve according to the sixth embodiment is shown in FIGS. The sixth embodiment differs from the first embodiment in the configuration of the supply check valve.

In the sixth embodiment, similarly to the supply check valve 71 of the first embodiment, the supply check valve 73 is formed in a substantially cylindrical shape by bending, for example, a rectangular metal thin plate so that the longitudinal direction is along the circumferential direction. FIG. 16 is a developed view of the supply check valve 73. FIG. 17 is a view of the supply check valve 73 viewed from the axial direction.

In the sixth embodiment, the supply check valve 73 includes an overlapping part 700, a valve part 701, and a notch part 731.
The overlapping portion 700 is formed at one end portion of the supply check valve 73 in the circumferential direction. The overlapping portion 700 is formed so as to overlap the radially outer end of the other circumferential end of the supply check valve 73 (see FIG. 17). Four valve portions 701 are formed at equal intervals in the circumferential direction of the supply check valve 71.

The notch portion 731 is formed so that both end portions of the supply check valve 73 in the axial direction are notched in the axial direction. A plurality of notches 731 are formed at intervals in the circumferential direction of the supply check valve 73.

The supply check valve 73 is provided in the circumferential flow path portion 503. The supply check valve 73 is provided so as to be elastically deformable in the radial direction at one end of the axial channel portion 502 and the circumferential channel portion 503. Here, the supply check valve 73 is provided so that the four valve parts 701 correspond to the four supply flow path parts 501 respectively. That is, the supply check valve 73 is provided on the radially outer side of the inner sleeve 50 with respect to the supply flow path portion 501.

When the supply check valve 73 is deformed so as to expand outward in the radial direction, that is, the inner diameter is increased, the overlapping portion 700 is separated from the other end of the supply check valve 73.
When the supply check valve 73 is deformed radially outward or radially inward, the hydraulic oil can flow through the notch 731. Therefore, it is possible to suppress the hydraulic oil in the vicinity of the end portion of the supply check valve 73 on the movement restricting portion 57 side from inhibiting the radial deformation of the supply check valve 73. Thereby, the operation | movement of the on-off valve of the supply check valve 73 can be made smooth.

(Seventh embodiment)
A part of the hydraulic oil control valve according to the seventh embodiment is shown in FIGS. The seventh embodiment differs from the second embodiment in the configuration of the outer sleeve 40, the inner sleeve 50, the supply check valve, and the like.

In the seventh embodiment, two supply flow path portions 401 are formed at equal intervals in the circumferential direction of the outer sleeve 40 (see FIGS. 18 and 19). The hydraulic oil from the oil pump 8 flows through the supply flow path portion 401.

The axial flow path portion 502 is formed to extend in the axial direction between the outer sleeve 40 and the inner sleeve 50.
The axial flow path portion 502 is formed on the fitting boundary surface T 1 between the outer sleeve 40 and the inner sleeve 50 so as to be recessed radially inward from the outer peripheral wall of the inner sleeve 50.

In the present embodiment, two axial flow path portions 502 are formed at equal intervals in the circumferential direction of the inner sleeve 50 (see FIGS. 18 and 19).
Each of the two supply flow path portions 401 connects one end side of each of the two axial flow path portions 502 and the outside of the outer sleeve 40. That is, the supply flow path portion 401 is open on one end side of the axial flow path portion 502.
In the seventh embodiment, the circumferential flow path portion 503 shown in the second embodiment is not formed.

The radial flow path portion 504 is formed so as to penetrate the inner sleeve 50 in the radial direction, and has one end connected to the other end side of the axial flow path portion 502 and the other end side connected to a space inside the inner sleeve 50. (See FIG. 18). Two radial flow path portions 504 are formed so as to be connected to each of the two axial flow path portions 502 (see FIG. 18).

The supply check valve 74 is formed by, for example, alternately bending a rectangular thin metal plate a plurality of times in the longitudinal direction.
The supply check valve 74 is provided on one end side of the axial flow path portion 502. The supply check valve 74 is provided at one end of the axial flow path portion 502 so as to be elastically deformable in the radial direction of the inner sleeve 50. Here, a total of two supply check valves 74 are provided so as to correspond to the two supply flow path portions 401. That is, the supply check valve 74 is provided on the radially inner side of the outer sleeve 40 with respect to the supply flow path portion 401.

The supply check valve 74 has a force that extends radially outward of the inner sleeve 50. Therefore, the supply check valve 74 abuts on the valve seat surface 44 and closes the supply flow path portion 401.

In the seventh embodiment, the valve seat step surface 45 and the stopper step surface 55 shown in the second embodiment are not formed.
When the hydraulic oil flows to the axial flow path section 502 via the supply flow path section 401, the supply check valve 74 is pushed by the hydraulic oil and deforms so as to shrink inward in the radial direction of the inner sleeve 50. As a result, the supply check valve 74 is separated from the valve seat surface 44, and the hydraulic oil passes between the supply check valve 74 and the valve seat surface 44, that is, on the other end side of the axial flow path portion 502, that is, , It can flow to the radial flow path portion 504 side.

When the flow rate of the hydraulic oil flowing through the supply flow path portion 401 becomes a predetermined value or less, the supply check valve 74 is deformed so as to extend outward in the radial direction of the inner sleeve 50, abuts on the valve seat surface 44 and closes. Thereby, the flow of the hydraulic oil from the axial direction flow path part 502 side to the supply flow path part 401 side is regulated.

In this way, the supply check valve 74 functions as a check valve, allows hydraulic oil to flow from the supply flow path portion 401 side to the axial flow passage portion 502 side, and is supplied from the axial flow passage portion 502 side. It is possible to regulate the flow of hydraulic oil to the flow path portion 401 side.

The movement restricting portion 56 is formed on the side opposite to the locking portion 59 with respect to the supply check valve 74. When the movement restricting portion 56 abuts on the supply check valve 74, the movement restricting portion 56 can restrict the movement of the supply check valve 74 to the side opposite to the axially engaging portion 59 of the inner sleeve 50.
The movement restricting portion 57 is formed on the locking portion 59 side with respect to the supply check valve 74. The movement restricting portion 57 can restrict the movement of the inner sleeve 50 of the supply check valve 74 toward the engaging portion 59 in the axial direction when contacting the supply check valve 74.

Thus, the

movement restricting portions

56 and 57 can prevent the supply check valve 74 from moving in the axial direction of the inner sleeve 50 and leaving the supply flow path portion 401. Further, the movement restricting section 56 can prevent the supply check valve 74 from moving to the other side of the axial flow path section 502 and closing the radial flow path section 504.

(Other embodiments)
In the embodiment described above, the movement restricting portion 56 that can restrict the movement of the supply check valve toward the locking portion 59 in the axial direction, that is, the other end side of the axial flow passage portion 502, and the shaft of the supply check valve The movement restricting portion 57 capable of restricting the movement to the opposite side to the direction locking portion 59, that is, the opposite side to the other end of the axial direction flow passage portion 502 is shown. On the other hand, in another embodiment of the present disclosure, one of the movement restriction unit 56 and the movement restriction unit 57 may be formed. Further, neither the movement restriction unit 56 nor the movement restriction unit 57 may be formed.

In another embodiment of the present disclosure, the valve seat step surface and the stopper step surface may not be formed.
In the above-described embodiment, the example in which the radial flow path portion 504 is formed so as to penetrate the inner sleeve 50 in the radial direction has been described. On the other hand, in other embodiments of the present disclosure, the radial flow path portion 504 may be formed so as to penetrate the outer sleeve 40 in the radial direction. In this case, the end of the radial flow path portion 504 opposite to the axial flow path portion 502 may be directly connected to the hydraulic oil supply target without passing through the inner sleeve 50.

Further, in the above-described embodiment, an example in which the axial flow path portion 502 is formed on the fitting boundary surface T 1 between the outer sleeve 40 and the inner sleeve 50 so as to be recessed radially inward from the outer peripheral wall of the inner sleeve 50. Indicated. On the other hand, in another embodiment of the present disclosure, the axial flow path portion 502 is on the fitting interface T1 between the outer sleeve 40 and the inner sleeve 50 so as to be recessed radially outward from the inner peripheral wall of the outer sleeve 40. It may be formed.

In the above first to third and seventh embodiments, the outer sleeve 40 is formed of a material containing iron, and the inner sleeve 50 is formed of a material containing aluminum. On the other hand, in other embodiments of the present disclosure, the inner sleeve 50 may be formed of any material as long as it has a lower hardness than the outer sleeve 40. Further, the outer sleeve 40 may be formed of any material as long as the material has higher hardness than the inner sleeve 50.

In the above-described fourth embodiment, the outer sleeve 40 is formed of a material containing iron, the first inner sleeve 511 is formed of resin, and the second inner sleeve 512 is formed of a material containing iron. . On the other hand, in other embodiments of the present disclosure, the first inner sleeve 511 may be formed of any material as long as it has a lower hardness than the outer sleeve 40 and the second inner sleeve 512. . Further, the outer sleeve 40 may be formed of any material as long as it has a higher hardness than the first inner sleeve 511. The second inner sleeve 512 may be made of any material as long as it has a higher hardness than the first inner sleeve 511.

Further, in another embodiment of the present disclosure, the hydraulic oil control valve 11 is not limited to the central portion of the vane rotor 30 and may be provided outside the valve timing adjustment device 10. In this case, the outer sleeve 40 can omit the screw portion 41. In this case, both the outer sleeve 40 and the inner sleeve 50 may be formed of a material containing aluminum. In this case, the material cost can be reduced while ensuring the strength of the outer sleeve 40 and the inner sleeve 50.

In another embodiment of the present disclosure, the outer sleeve 40 and the inner sleeve 50 may not include the first control port 411 and the second control port 412 and may not include the spool 60. In this case, the radial flow path portion 504 is formed in the outer sleeve 40 or the axial flow path portion 502 is opened at the axial end surfaces of the outer sleeve 40 and the inner sleeve 50 and connected to the hydraulic oil supply target. That's fine.

Further, the hydraulic oil control valve 11 of the present disclosure is not limited to the valve timing adjustment device 10 having two hydraulic chambers, the retard chamber 201 and the advance chamber 202, and is an operation that supplies to other devices driven by hydraulic oil. It may be used to control the oil.
In another embodiment of the present disclosure, the housing 20 and the crankshaft 2 may be connected by a transmission member such as a belt instead of the chain 6.

In the above-described embodiment, an example in which the crankshaft 2 is the “first axis” and the camshaft 3 is the “second axis” has been described. On the other hand, in another embodiment of the present disclosure, the crankshaft 2 may be a “second shaft” and the camshaft 3 may be a “first shaft”. That is, the vane rotor 30 may be fixed to the end of the crankshaft 2 and the housing 20 may rotate in conjunction with the camshaft 3.

The valve timing adjusting device 10 of the present disclosure may adjust the valve timing of the exhaust valve 5 of the engine 1.
Thus, the present disclosure is not limited to the above-described embodiment, and can be implemented in various forms without departing from the gist thereof.

This disclosure has been described based on embodiments. However, the present disclosure is not limited to the embodiments and structures. The present disclosure also includes various modifications and modifications within the equivalent scope. Also, various combinations and forms, as well as other combinations and forms including only one element, more or less, are within the scope and spirit of the present disclosure.

Claims

A hydraulic oil control valve (11) capable of controlling the flow of hydraulic oil supplied from the hydraulic oil supply source (8) to the hydraulic oil supply target (10),
A cylindrical outer sleeve (40);
A cylindrical inner sleeve (50) provided inside the outer sleeve;
A supply flow path portion (501) formed so as to penetrate the inner sleeve or the outer sleeve in the radial direction, and through which hydraulic oil from the hydraulic oil supply source flows;
An axial flow path portion (502) formed so as to extend in the axial direction between the outer sleeve and the inner sleeve, the supply flow path portion opening on one end side, and the other end side being connectable to the hydraulic oil supply target. )When,
In the axial flow channel portion, provided radially outside the inner sleeve or radially inner side of the outer sleeve with respect to the supply flow channel portion, the operation from the supply flow channel side to the axial flow channel side A supply check valve (71, 72, 73, 74) capable of allowing the flow of oil and regulating the flow of hydraulic oil from the axial flow path side to the supply flow path side;
Hydraulic oil control valve comprising.
The hydraulic oil control valve according to claim 1, further comprising a movement restricting portion (56, 57) capable of restricting movement of the supply check valve in the axial direction.
A circumferential channel portion (503) formed in an annular shape extending in the circumferential direction from one end of the axial channel portion between the outer sleeve and the inner sleeve;
The supply check valve (71, 72, 73) is formed in a cylindrical shape, and is provided so as to be elastically deformable in a radial direction at one end of the axial flow path portion and the circumferential flow path portion,
The axial direction flow path portion is formed around the opening of the supply flow path portion and faces the valve seat surface (52, 44) with which the supply check valve can contact, and the opening of the supply flow path portion. The hydraulic oil control valve according to claim 1 or 2, further comprising a stopper surface (42, 54) formed at a position and capable of restricting radial deformation of the supply check valve when the supply check valve contacts.
The axial flow path portion is formed on the other end side of the axial flow path portion with respect to the valve seat surface, on the radially outer side of the inner sleeve or on the radially inner side of the outer sleeve with respect to the valve seat surface. The hydraulic oil control valve according to claim 3, which has a valve seat step surface (53, 45).
The axial flow path portion is a stopper step formed on the other end side of the axial flow path portion with respect to the stopper surface, on the radially outer side of the outer sleeve or on the radially inner side of the inner sleeve with respect to the stopper surface. The hydraulic oil control valve according to claim 3 or 4, having a surface (43, 55).
The hydraulic oil control valve according to claim 5, wherein a boundary (B1) between the stopper surface and the stopper step surface is located within a range of an axial length of the supply check valve.
A valve closing assist passage portion (509) formed so as to penetrate the inner sleeve or the outer sleeve in the radial direction, having one end opened to the stopper surface, and into which hydraulic oil can flow inside is further provided. The hydraulic-oil control valve as described in any one of these.
A radial flow path portion (formed so as to penetrate the inner sleeve or the outer sleeve in the radial direction, one end connected to the other end side of the axial flow path portion and the other end side connected to the hydraulic oil supply target ( The hydraulic oil control valve according to any one of claims 1 to 7, further comprising: 504).
The outer sleeve has an inner peripheral wall formed in a cylindrical surface shape,
The inner sleeve has an outer peripheral wall formed in a cylindrical shape,
The axial flow path portion is on a fitting boundary surface (T1) between the outer sleeve and the inner sleeve so as to be recessed radially inward from the outer peripheral wall of the inner sleeve or radially outward from the inner peripheral wall of the outer sleeve. The hydraulic oil control valve according to any one of claims 1 to 8, wherein the hydraulic oil control valve is formed.
The outer sleeve has, on the outer peripheral wall, a thread portion (41) that can be screw-coupled to the inner wall of the hydraulic oil supply target,
The inner sleeve is formed of a material having a lower hardness than the outer sleeve,
The hydraulic oil control valve according to claim 9, wherein the axial flow path portion is formed in the inner sleeve.
The outer sleeve is formed of a material containing iron,
The hydraulic oil control valve according to claim 10, wherein the inner sleeve is made of a material containing aluminum.
The outer sleeve has, on the outer peripheral wall, a thread portion (41) that can be screw-coupled to the inner wall of the hydraulic oil supply target,
The inner sleeve includes a cylindrical first inner sleeve (511) formed of a material having a lower hardness than the outer sleeve, and the first inner sleeve formed of a material having a higher hardness than the first inner sleeve. A cylindrical second inner sleeve (512) provided on the inner side of
The hydraulic oil control valve according to claim 9, wherein the axial flow path portion is formed in the first inner sleeve.
The outer sleeve is formed of a material containing iron,
The first inner sleeve is made of resin,
The hydraulic oil control valve according to claim 12, wherein the second inner sleeve is formed of a material containing iron.
The hydraulic oil control valve according to any one of claims 1 to 9, wherein the outer sleeve and the inner sleeve are formed of a material containing aluminum.
The outer sleeve and the inner sleeve have control ports (411, 412) formed to connect to the hydraulic oil supply target,
A supply which is provided inside the inner sleeve so as to be capable of reciprocating in the axial direction, forms an internal space (600) on the inner side, and is formed so as to be able to connect the internal space and the other end side of the axial flow path portion. An oil passage (601), and a control oil passage (611, 612) formed so as to be connectable between the internal space and the control port, and the control oil passage and the control according to the position with respect to the inner sleeve The hydraulic oil control valve according to any one of claims 1 to 14, further comprising a cylindrical spool (60) that can be switched between connection and disconnection with a port.
A valve that is provided in a power transmission path for transmitting power from the drive shaft (2) to the driven shaft (3) of the internal combustion engine (1) and adjusts the valve timing of the valves (4, 5) that are driven to open and close by the driven shaft. A timing adjustment device (10) comprising:
When one of the drive shaft and the driven shaft is a first axis and the other of the drive shaft and the driven shaft is a second axis,
A housing (20) that rotates in conjunction with the first shaft, engages with an end of the second shaft, and is rotatably supported by the second shaft;
The vane (32) is fixed to the end of the second shaft and partitions the space (200) inside the housing into a plurality of hydraulic chambers (201, 202), from the hydraulic oil supply source to the hydraulic chamber. A vane rotor (30) that rotates relative to the housing in response to the pressure of the supplied hydraulic oil;
A hydraulic oil control valve (11) according to claim 15,
The hydraulic oil supply target is the valve timing adjusting device,
The control port is a valve timing adjusting device connected to the hydraulic chamber.
The valve timing adjusting device according to claim 16, wherein the hydraulic oil control valve is provided in a central portion of the vane rotor.